Double-acting power-pump.



W., lKlmzwoonl DOUBLE ACTING POWER PUMP. APPLICATION FILED SEPT. 17,1906.

ril: N JRRIs PETERS o sHlNcrn n c W. 4KIRKWOOD. DOUBLE ACTING PoWERPUMP.

APPLICATION ILED SEPT. 17, 1906. 899,541 Patented sept .29,1908. aSHEETS-SHEET 2.

u. tl... lill.'

Illll' Illlllilll NI Illlll Illllllll H W. KIRKWOOD. DpUBLE AOTING POWERPUMP. APPLICATION IILEDBEPT. 17, 19128-1 3 SHBETB-SHBET 3.

899,541; J Patented sept. 29, 1908.

NITED PATENT OFFICE.

WILLIAMIKIRKWOOD, OF CHICAGO, ILLINOIS.

i DOUBLE-ACTING POWER-PUMP.

NCQ 899,541.

Specification of Letters Patent.

Patented sept. 29, 190s.

Application led September 17, 1906. Serial No. 334,891.

new and useful Improvements in Double-` Actin Power-Pumps, of which thefollowing is a fu l, clear, and exact specification.

This invention relates to improvements in double acting power pumps inwhich heretofore there has been a crank-arm, rod, or other flexibleconnection between the pistons of the power cylinder and the pumpcylinders, and in fact, two suchconnections in duplex pumps, and also topower pumps in which the power controlling valve is mechanicallyconnected with the pump cylinders as a means for actuating the powervalve off its dead centers.

The prime object of my invention is to alternately actuate the power andpump pistons of a double acting pump by substantially a directapplication to both, of the motive force employed to o erate them.

Another and importante ject of my invention is to alternately actuatethe power and pump pistons of a double acting pump by the motive forceemployed to operate them, and to control such force with a single valve.

A still further and important obj ect of my vinvention is to havea'shifting mechanism,

for the valve controlling the power piston or istons of a pump, actuatedpartlyin both Tdirections of its movements by the pump piston orpistons, which mechanism in turn is actuated by its own power toshiftand positively shifts the valve throughout both its movements. Y

With these ends in view,y my invention consists in certain features ofnovelty in the construction, combination and arrangement of parts, bywhich the said objects and certain other objects hereinafter appearingare attained, all as Afully described with reference to the accompanyingdrawings, and` more particularly ointed out in the claims.

In the sai drawings: Figure 1 represents a vertical central longitudinalsection through a power y Fig. 2 a etail 4thereof showing the duplexinlets in the seat ofthe valve controlling the supply of motive forcethereto. Fig. 3a detall transverse section through the controlling valvefor the motive force and vertically through one of the inlets andoutlets in the ump embodying my invention.

seat thereof. Fig. 4 a side elevation of the valve controlling themotive force and showing the relative position of the inlets thereinthrough which the motive force is supplied to joined power pistons, thone of which is isolated from the other. Fig. 5 a detail side elevationmainly showing the controlling defvices for the valve of the powerpistons and one ofthe connecting rods for the pump pistons. Fig. 6 adetail reverse front elevation of the valve controlling devices, withthe oscillating piston therefor removed and showing the engagement ofthe sliding rack with its pinion. Fig. 7 a transverse section partly insection centrally through the valve and the supply inlet therefor withdotted lines indicating the position of one of the exhaust inlets fromthe power pistons for the motive force. Fig. 8 afront elevation with aportion of the pump cylinders omitted showing a modification of themeans for actuating the controlling valve and keeping the valve off deadcenters or stationary on any point of its travel.

Similar-characters of reference indicate the same parts in the severalfigures of the drawings.

My invention contemplates the employment of two end to end cylindersisolated from each other by their heads and open at their opposite ends,but in practice a single cylinder 9 divided into two power pistonchambers 10y and 11V by a single head 12 is employedwith the outer endsof Asaid cylin-` ders opening for their full diameters into pumpcylinders 13 and 14 respectively, which several cylinders may besupported upon standards 15 and 16 resting upon a floor or other baseand by screwing them into sockets formed with the castings of suchcylinders and preferably at the junction of the pump cylinders with thepower cylinders.

Respectively working in the power cylinders 10 and 11 are elongatedpistons 17 and 18, each of which are provided with cupshaped packings19-19 and preferably of leather but may be of other material held in'place across the end of the piston and also in shape by hanged screws20-20 seated in the piston. The pistons 17 and 18 have secured theretoor formed integral therewith pump pistons 21 and 22, and are providedtransversely with inlets 23-23 bisected by axial dassages 24 extendingthrough the pistons 21 and 22 respectively.

Pump cylinders 13 and 14 are provided with rear-end openings 25-25 butinstead of such openings said pump cylinders may be provided with aseries of perforations adjacent their opposing inner ends through whichthe liquids or gases to be compressed may be supplied to the transverseinlets in the body of the power pistons. The axial passages 24-24,through which is supplied to the compressing chambers of the pumpcylinders the materials to be compressed or pumped, are respectivelycontrolled by inlet valves 26-26 mounted upon straps 27H27, the seats28-28 for which valves are inclined and project respectively from thefaces of the pistons 2l and 22.

Straps 27-27 are formed from cup packings 29-29 by suitable parallel andtransverse slits and held in place by rings 30 clamped upon the packingsand to the pistons 21-21 by screws 31-31, screwed into the pistons, butthe straps for the valves may be in pieces separate from the pistonpackings and the piston packings be of any material or shape without anysubstantial departure from my invention.

The outer ends of the pump cylinders 13 and 14 are respectively closedby heads 32-32 between which and the ends of said cylinders are gaskets33-33, said heads being secured to the ends of the cylinders in theusual manner by screws 34-34 which may be of any number necessary tothat end, and are provided with valve chambers 35-35 having a contractedoutlet axial in the head and into which are screwed discharge pipes36h36.

Opposing the inner faces of the pump cylinder heads 32-32 are plates37-37 which are preferably flat but may be cup shape in form to fit acorresponding recess in the heads, and with their anges 38 abuttingagainst the ends of the cylinders when the heads are tightened to place,which plates 37 serve to clamp against' the cylinder head packings 39-39through which and through the plate are openings 40-40 preferablyregistering with the pipes 36-36, and opened and closed by valves 41-41faced with straps 42-42 to which the valves are secured by screws 43passing through the strap and screwed into the valve.

The straps 42 may be formed in the manner described as to the straps 27of the valves 26 so as to form a packing for the valve 41 seatingagainst an inclined seat formed on the plate 37. In this connection itis proper to add that ordinary cheek valves may be substituted for thestrap valves without a substantial departure from my invention, and thatboth valves swing in the same direction in opening and closing, but thatin operation when the valves 26 are closed the valves 41 are open aswill be understood by referring to the right of Fig. 1 in which thepiston 22 has just started on its return movement with the result thatthe iii-rushing liquid or gas, at its as may be, through the inlet 23and axial passage 24 has by its force unseated the valve 26 and the backpressure in the pipe seated the outlet valve 41V whereas at the left ofFig. 1. the inlet valve 26 is seated by the pressure ol the liquid orair as may be in the elnnnber in the pump cylinder and the valve 4-1 isslightly open.

In order that the cup packings 1.) of the power pistons may bemaintained with desired tightness in the pistons 1() and 11, the edgesof the flanges thereof are inclined as indicated at 43 and opposed bycorresponding bevels 44 on the head 12 so that at the limit of everycomplete stroke of the pistons the inclined edges of the packingscontact with the bevels of the head and are pressed outwardly andthereby continuously maintained in that position, and at the same timeprevented from jamming between the pistons and the cylinders. ln theheads 12 and on both sides thereof are recesses 45 for receiving theprojected heads of the flange screw plates 20 and thereby provide forthe contact above described of the edges of the paekings 19 with thebevels 44.

Motive force for actuating power pistons and simultaneously therewiththe pump pistons is supplied to the cylinder 1() (see Figs. 1 and 2)through an inlet 46 and exhausted therefrom from the port 47 to and fromthe cylinder 11 (see Fig. 2) through the inlet 48 and exhaust port 49,which inlets and ports so far described are formed (see Fig. 1) in atubular standard 50 at the junction of the cylinders and which alsoforms a seat for a rotary valve 51 (see Fig. 4) provided with an inlet52 and two exhaust ports 53 and 54 between which in the body of thevalve there is no communication, for the inlet 52 of the valve extendstransversely entirely through the valve, whereas the exhaust ports 53and 54 open into a chamber 55 (see Fig. 7) inr the body of the valvecommunicating with a discharge cock 56, but which may be a pipeconducting the exhaust motive force to any desired point away from thepower cylinders, the motive force being supplied thereto through a pipe57 in which there is a stop cock and may be a globe valve 58 forregulating and cutting off the supply of motive force, and forregulating the supply of steam to an oscillating piston structure whichwill now be described.

Stop cock or globe valve 58, as may be, is of the ordinary structure andprovided with a hand-hold 59, and furthermore with a transversepassage,not shown, bisecting the supply passage therein which transverse passageextends longitudinally in a projection 60, which is bisected by acylinder 61 oscillating thereon, and held against detachment by a screw62, which cylinder projects downwardly and has an elongated piston 63,which lower end is pivoted upon a crank pin 64, secured on the outerface and towards the periphery of a pinion 65, the teeth of which areformed by laterally projecting'. pins 66 which, as shown in thedrawings, are three in number but for the purpose of their operation maybe of any other number. Pinion 65 is secured to ahub 67 sleeved on thestem of the valve 51.

Rigidly secured on the rojecting stem end of the valve 51 is a cranll;plate 68, the arm 69 of which projects into a segmental slot 70 inthepinion as clearly shown in Figs. 5 and 6, and for the purposes presentlyto be de- The pump pistons 21 and 22 are rigidly connected by rods 71and 72 (see Figs. 5 and 7) to one of which is rigidly secured twoparallel uprights 73 and 74 (see Figs. 1 and 5) united at their upperends by an angular bar 75 which is screw-threaded towards each end atpoints between the standard (see Fig. 6) as shown at 76A and has onthese screwthreaded portions adjustable nuts 77 and 78.

Supporting and sliding upon the bar 75 is a rack 79 provided withopposing teeth 80 and 81 adapted to alternately engage the teeth 66 ofthe pinion 65 and to have the length of its stroke increased anddecreased by means of the adjustable nuts 77 and 78 and whereby therapidity of the shifting of the valve is increased or diminished andmaintained at any desiredgiven number of strokes per minute.

In order to maintain the valve 51 closely seated and to take up wear, as ring 82 (see Fig. 7) is sleeved thereon and as one end abuttingagainst a shoulder formed by a large recess in the hub 67, and its outerend bearing against the crankplate 68 rigid on the valve sleeve, thetendency of the spring being to tighten the valve in its seat owing tothe fact that both the valve and the seat correspondingly taper on linesconverging towards the crank plate.

In operation with the parts in the position shown in Fig. 1, the motiveforce is flowing down through the pipe 57, the valve, and the inlet 46into the cylinder 10 against the piston 17, during the time of whichflow the port 47 is closed as is also the inlet 48 of the cylinder 11,while its rport 49 is open, and discharging exhaust into the chamber 55of the valve and thence onward to its destination. As this supply ofmotive force con-- tinues, the power piston 17, and simultaneously withit the lpump piston 21, arel dium of the connecting rods 71 and 72, thepower piston 18 and the pump piston 22 will simultaneously be pulledinwardly to the limit of their inner or back stroke when the cup packing19 will engage the annular bevel 44 on the head 12, and be therebyforced outwardly and tightened against the walls of lthe cylinder 11. Atthe moment the piston 17 begins to move towards the limit of its outwardstroke, as just described, the cylinder 61 and iston 63 of theoscillating piston, are in t e inclined position shown in Fig. 1 and atthe limit of their downward movement, and the slidingrack 79 is at thelimit of its stroke and out of engagement with the pinion, but as thepiston 17 continues its outward movement, the rack, by reason of itssupport from the connecting rods of the pump pistons and its engagementby the adjustable nut 77, is gradually moved to engagement with thepinion and thereafter rotates the pinion 65 against the resistance ofthe stroke of the oscillating piston until the instant that piston hasmoved to the limit of its upward stroke to and beyond a verticalposition, which is its dead center, when the expansion of the motiveforce therein will quickly swing it downwardly to the limit of its otherand opposite `down stroke, and cause the pinion to as quickly carry thesliding rack onward to the limit of its stroke, and in position to beagain moved to engagement with the pinion during the return or inwardstroke of the piston 17, and in the same manner and by the same meansthat caused its engagement therewith as above described occurred. At thetime the piston 17 began its outward thrust movement, as just described,and at which time the motive force was flowing into the valve 51, theposition of the crank arm 69 in the slot 70 was reversed from that whichit now occupies in Fig. 5, the result being that the valve wasstationary until after the sliding rack had moved the oscillating pinionbeyond its Adead center towards the position shown4 in Fig. 5, and hadby the expansion 0f the motive force therein quickly shifted theposition of the pinion until the end wall of its slot engaged and swungthe crank arm to the right to the position shown in Fig. 5, in whichposition ofthe crank arm, the pinion and the oscillating piston,thevalve 51 is reversed from that shown in Fig. 1, that is to say, motiveforce is flowing through the valve and the inlet 48 into the cylinder 11and against the piston 18, while in the meantime its port 49 is closedand the port 47 of the piston chamber 10 is opened. In other words, thevalve is shifted by the operation of the oscillating piston and not bythe operation of either 'the pump or power piston which serves onlyansion of the motive force therein to oscilate the pinion, and at thesame time disengage it from its rack bar so that the power and pumppistons make a substantial portion of their stroke in both directionswithout causing any movement of the valve, and in fact make both oftheir strokes in the absence of any connection with the valves or whichis directly concerned in its shifting for the movement of the valve asdependent upon and its shifting entirely produced by the action of theoscillating piston structure.

As shown in Fig. 8, a spring may be substituted and perform thefunctions of the oscillating piston in which construction, however, twogears are necessarily employed, one of which gears is provided with aradial slot and carries the crank Aarm engaging therewith, while theother gear carries the pinion and the position of the rack bar isreversed from a depending to an upwardly projecting position. In saidFig. 8, 83 and S4 indicate two intermeshing gears, the upper of whichgears 83 is pivoted on a stud S5 projecting from the pipe 57 moreclearly shown in Fig. 7, and the lower gear upon the projection 67, theinternal bore of which provides a bearing for the valve stem whichprojects outwardly beyond the same and has secured thereto a bell crankplate 86, the crank arm 87 of which projects into a segmental slot S8 inthe gear S4 which crank arm and its plate and the slot are similar inevery respect to the crank arm 68 and slot 70 in Figs. 5 and 6. Theupper gear S3 is provided with lateral projecting pins S9, three innumber, and which correspond with the teeth of the pinion 65 in Figs. 5and 6, and so arranged that they may be engaged by a sliding rack 90supported and operating precisely the same as the corresponding rack 7 9in Figs. 1, 5 and 6, except that its teeth project upwardly above thesame in Fig. 8 whereas they project below as shown in the three figuresabove mentioned. Projecting outwardly from the gears S3 and 84 are studsor pins 91 and 92 respectively, and to which are secured at its oppositeends a coil spring 93, the operation of which is substantially the samein effect upon the gears and their cooperating parts as that of theoscillating piston first described. For example, when the spring 93 isin the position it is shown to have in Fig. 8 its tension serves tomaintain both gears at one limit of their oscillation, as does thevibrating piston when in substantially the same position, but as thepump and power pistons move from the limit of one stroke towards theother, the sliding rack bar 90 engages the pinion teeth 89 and revolvesthe gears against the resistance of the spring 93 until the gears havepassed their dead centers when the force of the spring will actuate andinstantly force the gears to the opposite limit of their oscillation butbefore they have reached that limit the arm 87 of'the bell crank willhave engaged the end wall of the slot 88, and as quickly shifted thevalve to its second position as before described in connection withFigs. l to 7 inclusive. In this connection it is proper to add thatinstead of employing the motive force used for the power pistons toactuate the oscillating piston, and which may be steam, gas, etc., aspring con'lined within the oscillating cylinder may he employed so thatit will be compressed by the inward thrust of the piston and expanded bythe retraction of the piston, but whether this substitution is made ornot, it is obvious that such an oscillating piston structure is themechanical equivalent of the spring employed in the structureillustrated in Fig. 8, because the operation of the auxiliary pistonwith regard to the pinion and the valve is precisely the same andproduces the same results in both instances.

In both forms of structure shown it should be noted that the lost motionwhich occurs between the valve and the stops therefor against the endwalls of the pinion-slot provides for maintaining the valve againstmovement untilv the power and pump pistons have reached the limit oftheir strokes and that the valve may be instantly shifted without anyundue dragging tending to retard that movement.

Although the connection between the valve and the auxiliary piston isprovided for by means of a slot in the pinion, it will be no substantialdeparture from the spirit of my invention to employ stop pins carried byradial arms, and instead of having the teeth of the pinion projectingfrom a plate they may be likewise carried by arms extending radiallyfrom a hub like structure similar to that which carries the pinion.Again it should be understood that my invention is not limited to theemployment of an oscillating plug-valve such as has been shown anddescribed, for it would not require the exercise of more than ordinarymechanical skill to connect the shifting mechanism with a rotary or asliding valve so that either of' said valves would be operated preciselythe same way and produce the same result as that accruing to theplug-valve shown and described.

Ihile I have shown and described a valve shifting mechanism of myinvention adapted for a double acting pump, it should be stated that itis also adaptable for single acting pumps in which a double end pistonis employed in the power cylinder and on the other hand it is apparentthat the employment of such a valve structure and shifting mechanismwhen applied to a double acting pump, such as is herein described, animportant advantage in cheapness, simplicity and certainty of operationfollows which it is desirable, for many reasons to secure.

. In conclusion it shoul'd be noted that the end to end arrangement ofthe power and pump cylinders and the connection with each other in adirect line with the pistons of the adjacent cylinder are productive ofmost important results in that not only is the actuating force forduplex power cylinders controlled by a single valve, but it is sodirected from a power cylinder to a pum cylinder that the pump pistonsmay be su stantially larger than the power pistons and be successfullyactuated by a corresponding less volume of power, as for example lessamount of steam at any given pressure, whereas before my invention thecommon practice has been to have the power pistons larger than the pumppistons or in any event not less than of the same'size.

Having described my invention, what I desire and claim by Letters Patentis 1. In a pump the combination oftwo pump cylinders, an intermediateduplex power cylinder separating and isolating said pumpl cylinders fromeach other, all of said cylinders being alined' end to end about acommon axis, pistons for each of said cylinders, piston` rods connectingin pairs the pistons of adjacent pump and power cylinders, a rod or rodsconnecting said pairs of pistons and a single valve controlling themotive fluid to power cylinders, substantially as described.

2. A pump comprising in combination two pump cylinders both of which areopen at one end, an intermediate power cylinder separating and isolatingsaid pump cylinders from each other, all of said several cylinders beingalined end to end about a common axis, pistons for each of saidcylinders, piston rods connecting in pairs the pistons for adjacent pumpand power cylinders, a rod or rods connecting said pairs of pistons, andmeans controlling the motive fiuid to both power cylinders,substantially as described.

3. A pump comprising in combination two pump cylinders, an intermediateopen-end y duplex power cylinder between and separating said pumpcylinders from each other, all of said cylinders being alined end to endabout a common axis, pistons for each of said cylinders, piston rodsconnecting in pairs the pistons for adj acentpump and power cylinders, arod connecting said pairs of pistons, and means controlling the motivefluid to both power cylinders, substantially as described.

4. A pump comprising in combination two pump cylinders, intermediateduplex power cylinders between and isolating said pump cylinders fromeach other, the opposing ends of said cylinders being-open and all ofsaid cylinders being alined end to endabout a common axis, pistons foreach of said cylinders, iston rods connecting in pairs pistons foradjacent power and pump cylinders, a rod or rods connecting said pairsof pistons,

and means controlling the motive Huid to both cylinders, substantiallyas described.

5. A pump comprising in combination two pump cylinders, two open endpump cylinders, an intermediate open end duplex power rcylinder betweenand isolating said pump cylinders from each other, said severalcylinders being formed integrally with each other, adjacent pump andpower cylinders opening into each other and arranged end to end about anaxis common to all, pistons for each` of said cylinders, piston rodsconnecting in pairs the pistons for adjacent power and pump cylinders, arod or rods connecting said pairs of pistons, yand a single valvecontroling the motive fluid to both power cylinders, substantially asdescribed.

6. A pump comprising in combination two open end pump cylinders, anintermediate duplex power cylinder between and separating said pumpcylinders from each other, all of said several cylinders being alinedend to end about a common axis, plstons for each pairof said cylinders,pistonr rods connecting` in lpairs pistons of adjacent pump and power cyinders, a rod or rods projecting into the pump cylinders and connectingsaid pairs of' pistons, and means controlling the motive fluid to bothpower cylinders, substantially as described,

7. In a double acting pump two pump cylinders, intermediate powercylinders isolating said-pump cylinders, pistons for all of saidcylinders, piston rods connecting the pistons of adjacent power and pumpcylinders in pairs, said several cylinders being arranged end to end,the openings of the pump pistons being of substantially greater areathanY those of the power pistons, a rod or rods projecting into the pumpcylinder and connecting said pairs of pistons and a single valveAcontrolling the motive fluid to the l power pistons, substantially asdescribed.

8. In a pump the combination of two pump cylinders, intermediate powercylinders in end to end arrangement about an axis common to allrespectively and directly opening the one into the other, the powercylinders of substantially less diameter than the pump cylinders,correspondingly differentiating pistons for each of said severalcylinders, plston rods connectin the pistons of adjacent pump and powercylinders in pairs, and provided with passages for conducting fluidstherethrough, valves controlling the iiow of iiuids through said pistonrods and pump cylinders and a single valve controllin the motive Huid tothe power cylinders, su stantially as described. A

9, In a pump the combination with two open end single acting pumpcylinders, intermediate duplex open end power cylinders separating andisolating said pump cylinders from'each other, the several saidcylinders being arranged end to end about a common aXis and in opencommunication with each other, separate power and pump pistons for theadjacent pump and power pistons, means rigidly connecting said pump andpower cylinders with each other, separate inlet and outlet ports foreach power cylinder, a single valve controlling said ports andregulating the supply of motive fluid to the power cylinders actuatingthe pump cylinders, and means connecting said parts of pistons togetherand the valve with both pump and pistons, substantially as described.

-v 10. In a pump, the combination with single acting duplex pumpcylinders, intermediate duplex power cylinders, a valve controlling themotive iiuid therefor, a valve shifting mechanism and an adjustablesliding rack connection between the pump piston and the valve shiftingmechanism, substantially as described.

11. In a pump, the combinationwith a pump piston, a power piston, avalve controlling the motive fluid therefor, and a valve shiftingmechanism, of an adjustable slidable rack connection between the pumppiston and the valve shifting mechanism, substantially as described.

12. In a pump, the combination with a pump piston, a power piston, avalve controlling the motive fluid therefor, a valve shifting mechanismand a pinion therein, of a sliding rack adapted to engage said pinionand connect the pump piston with the valve shifting mechanism,substantially as described.

13. In a pump, the combination with a pump piston, a valve controllingthe motive fluid therefor, a valve shifting mechanism, a slotted piniontherein, and means connecting said pinion with the valve of a pumppiston, and a sliding rack connection between the pump piston and thevalve shifting mechanism, substantially as described.

l14. In a pump, the combination with a. pump piston, a valve'controlling the motive fluid therefor, a valve shifting mechanism aslotted pinion connection thereof with the valve, and a sliding rackadapted to engage said pinion, of a pump piston, and means whereby saidrack is connected with and actuated by the pump piston, substantially asdescribed.

15. In a pump, the combination with a pump piston, a valve controllingthe motive iiuid therefor and having dead centers, an oscillatingvalve-shifting mechanism automatically moving said valve olf its deadcenters, and means for storing power, of a pump piston, and anadjustable sliding rack connecting said piston with the valve-shiftingmechanism and whereby said mechanism is maintained ofi' its deadcenters, and power for actuating the valve is stored therein,substantially as described.

16. In a pump, the combination of a pump piston, a power piston, asingle valve having dead centers and controlling the motive fluidtherefor, a valve shifting mechanism, an adjustable sliding rackconnection between tlie pump piston and the valve shifting mechanism,and a spring moving said valve off its deadv centers, substantially asdescribed.

17. In a pump, the combination of a pump piston, a power piston, a valvecontrolling the motive fluid therefor, a valve-shifting mechanism havingtherein a sliding rack, a pinion and a spring having a bodily lateralmovement shifting the pinion oil its dead centers, substantially asdescribed.

In witness whereof, I have hereunto set my hand this 13th day ofSeptember, 1906.

WILLIAM IIIRKVVOOD.

In the presence of- E. K. MANCHESTER, JNO. G. E Lrrorfr.

